Spinning frame drive control



Dec. 8, 1936. P. B. REEVES PINNING FRAME DRIVE CONTROL 4 Filed Aug. 21, 1955 3 Sheets-Sheet l INVENTOR. faa/ fiiieerea ATTORNEYS 'P. B. REEVES Dec. 8, 1936.

SPINNING FRAME DRIVE CONTROL Filed Aug. 21, 1933 3 Sheets-Sheet 2 r? Q 35 I 7 I." i J? J INVENTOR. Pfill[.B.R

Dec. 8, 1936. P. B. REEVES 2,063,462

SPINNING FRAME DRIVE CONTRO L Filed Aug. 21, 1933 I 5 Shets-Sheet 3 INVENTOR. Paul 5.1766V5,

ATTORNEYS Patented Dec. 8, 1936 UNITED STATES Paul B. Reeves, Columbus,

Ind, assignor to Reeves Pulley Company, Columbus, Ind, a corporation of Indiana Application August 21, 1933, Serial No. 686,113

7 Claims.

The present application relates to drive mechanism for spinning frames, and more particularly to mechanism for automatically driving spinning frames at optimum variable speeds. The invention involves the provision of a variable speed drive for spinning frames, together with an automatic control for the variable speed drive; such control being of such character as automatically to vary the speed of the spinning frame: to which it is applied. to maintain that speed at an optimum high value throughout the cycle of operation of the spinning frame.

It has long been known that, in the operation of a spinning frame, as the thread or yarn builds up on the bobbins to increase the effective diameter of the bobbins, the tension on the yarn which exists between the travelers and the bobbins is reduced; and that therefore speed of operation can be increased as the tension is reduced, without causing an increase in the amount of breakage. If the machine is to be driven at a constant main shaft speed, obviously that speed must be slow enough throughout the winding of the bobbins so that breakage will not be unduly high at the beginning of the run when the tension is at a maximum. It follows that, during a large part of the run of the machine, the machine is operating at an inefficiently slow speedthat is, at a speed which is slower than necessary to prevent undue breakage. In actual practice, in the past, a compromise has been eifected, and the machines have ordinarily been driven at a speed which is higher than optimum for starting the wind, but which is lower than is feasible for other portions of the wind. As a result, the operation as a whole has taken a longer time than necessary, and there has been an unduly large amount of breakage during the early stages of the wind.

Furthermore, if a spinning frame: is operated at constant speed, whereby the tension between the travelers and the bobbins varies during the wind, obviously the size and strength of the thread being wound varies during the wind.

For both of these reasons, then, it is desirable to maintain an optimum tension between the travelers and the bobbins at all times, and that can be done only by gradually varying the speed of rotation of the bobbins as the bobbins are filled.

As is well known, there are two kinds of winding operations performed by spinning frames; via, the warp wind, and the filling wind. In the warp wind, the thread or yarn is laid on the bobbin in a plurality of layers, each of which extends substantially throughout the entire (Cl. i l-230.17)

length of the bobbin. In operating a spinning frame for warp winding, the ring rail travels substantially from the bottom of the bobbin substantially to the top of the bobbin upon each reciprocation.

In the filling wind, the thread or yarn is laid on the bobbins in substantially conical layers, the length of each of which, in the direction of the axis of the bobbin, is quite short. In operating a spinning frame to perform a filling wind, the ring rail is caused to reciprocate with a relatively short stroke, the upward component of each reciprocation being slightly longer than the downward component thereof.

The so-called combination wind is,. essentially a filling wind using a longer stroke than that used in a normal filling wind.

Obviously, when the spinning frame is in use for warp winding, the maintenance of substantially uniform tension throughout the wind requires that the machine be started at a speed which is lower than that which is used in practice in the use of constant speed machines, whereby breakage is materially reduced; and that speed of operation be increased as the wind pro-- ceeds; up to a predetermined point in the cycle of operation of the machine, whereafter the machine will be continued in operation at a predetermined optimum high speed until the run is completed.

On the other hand, when the machine is being used for filling winding, it is desirable to drive the spinning frame slowly at the beginning of the cycle, gradually increase the speed as the thread is built up to form inverted cone surfaces adjacent the lower portions of the bobbins; drive the frame at a constant, comparatively high speed as the thread is built up to form cylindrical surfaces over the mid portions of the bobbins; and gradually reduce the speed of the spinning frame as the thread is wound to form cone surfaces adjacent the upper ends of the bobbins. As has been said, in operating a spinning frame for filling winding, the ring rail is continuously reciprocated, the length of stroke of the ring rail being substantially constant, but such'stroke continuously changing its position. In other words, each upward movement of the ring rail is slightly longer than the succeeding downward movement so that, while each upward movement of the ring rail is substantially of the same extent as the preceding upward movement thereof, each succeeding upward movement will bring the ring rail to a new high position.

Attempts have been made, in the past, to control the speed of operation of spinning frames by driving the frames with variable speed motors; but the well-known disadvantages of variable speed motors in operation have resulted in failure of that idea to find a place in the practical art. Attempts have also been made in the past to control spinning frame speeds through the medium of complicated planetary gearing systems; but those attempts have also failed, due primarily to the inefficiency of such transmissions. The structure of the present application has been introduced to the practical art, and is already meeting with marked success.

As has been indicated, the object of the present invention is to provide mechanism which is capable of automatically controlling a variable speed drive in such a manner as to operate a spinning frame at optimum speed during either warp winding or filling winding. It is a further object of the invention to provide an organization of the character above outlined which shall be so designed as to perform the desired functions in the most advantageous manner possible, and which shall not be subject to the disadvantages of prior structures intended for similar purposes. Further objects of the invention will appear as the description proceeds.

To the accomplishment of the above and related objects, my invention may be embodied in the form illustrated in the accompanying drawings, attention being called to the fact, however, that the drawings are illustrative only, and that change may be made in the specific construction illustrated and described, so long as the scope of the appended claims is not violated.

Fig. l is a broken perspective view of one end of a spinning frame, having associated therewith a variable speed drive and a control therefor, constructed in accordance with the present invention;

Fig. 2 is a broken perspective view of the variable speed drive mechanism illustrated in Fig. 1;

Fig. 3 is a perspective view of the control mechanism for the variable speed drive illustrated in Fig. 1, parts being broken away for clarity of illustration;

Fig. 4 is a plan of a part of the control mech-. anism;

Fig. 5 is a central sectional View of a part of the control mechanism;

Figs. 6, '7 and 8 are broken plans of certain details of the control mechanism, the oscillating arm being shown in various positions which it assumes during its cycle; and

Fig. 9 is an enlarged elevation, partly in section, of a detail of construction.

Referring more particularly to the drawings, it will be seen that I have illustrated a spinning frame, indicated generally at it, and comprising an end frame or skeleton l, which assists in supporting a plurality of bobbin spindles l2. A ring rail-l3 is associated with said bobbin spindles, a traveler l4 carried by said ring rail being associated with each of said spindles. The thread or yarn i5 is led from the rovings |G through the travelers to the bobbins, and is built up on the bobbins as at ii. In Fig. 1, it will be obvious that a portion of a filling wind has been completed.

The ring rail is reoiprocated by a rod or plunger I8 which, in turn, is driven by the main shaft IQ of the spinning frame through an oscillating shaft 29 having an arm 2| to which said rod 58 is connected.

The shaft l9 carries, immediately beyond the frame I a coned disc 22 which is rigidly secured to the shaft. Splined on the shaft I9, and facing the disc 22, is a second coned disc 23, said disc 23 being constantly urged toward the disc 22 by a spring 24, one end of which bears against said disc 23 and the other end of which bears against a collar 25 carried on the hub 22 of disc 22.

A V-pulley 26 is carried upon the shaft 21 of a constant speed motor 28; and said motor is mounted upon a plate or carriage 29 which is slidably mounted in a guide-way 30 formed in a base member 3i.

A V-belt 32 forms a driving connection between the pulley 26 and the cone discs 22 and 23.

It will be clear that, as the plate 29 is shifted upwardly or downwardly in its guideway 30, the shaft 27 and pulley 26 will be moved toward and away from the shaft I9 and. discs 22 and 23. As the shaft 2i is moved toward the shaft l9, the tension on belt 32 is relaxed, whereby the spring 24 is permitted to move the disc 23 toward the disc 22, thereby increasing the effective diameter of the pulley formed by said discs 22 and 23. It will be clear that such increase in effective diameter will result in a reduction of the speed of the shaft I9. Correspondingly, movement of the shaft 21 away from the shaft it? will result in a reduction of the effective diameter of the pulley formed by the discs 22 and 23, with a consequent increase in speed of the shaft I9.

Referring, now, to Fig. 3, it will be seen that a collar 33, preferably provided with a lubricating unit 34, is threadedly mounted upon a threaded shaft 35, the lower end of said shaft being journaled in a bearing 36 preferably provided with a lubricating unit 37. Adjacent the lower end of said shaft 35 there is preferably provided a friction brake 38 for preventing possible overrun of said shaft 35. The plate 29 carries a pair of spaced lugs 39 through which the shaft 35 passes; but the bores of said lugs are not threaded, so that said lugs slide freely on said shaft. The collar 33 is snugly embraced between the lugs 39 so that, when said collar is moved upwardly or downwardly by rotation of the shaft 35, the plate 29 will be carried with it.

The upper end of said shaft 35 is, in the illustrated embodiment of my invention, formed to provide one element of a universal joint indicated at 4|, the lower end of a shaft 42 being journaled in a bearing 40 formed on the casing secured to said base 3|; and said end of said shaft 42 is formed to provide the other element of said universal joint. It will be readily understood that the universal joint is not essential, since the shafts 4| and 42 may, if desired, be positioned in alignment with each other. The shaft 42, suitably journaled in bearings provided therefor, has loosely mounted thereon a sprocket and said sprocket is provided with clutch teeth for cooperation with a clutch member 44 which is splined on said shaft 42. Said clutch member 44 is formed with a flange 45 against which bears one end of a spring 46, the opposite end of said spring bearing against a collar 41 fast on said shaft 42. The upper end of the shaft 42 is preferably formed to receive a manually-operable crank 48, whereby said shaft may be manually operated at times.

A standard 49 provides a pivot support for a clutch-operating lever 50 having a fork 5| embracing the clutch element 44 and bearing against the under surface of said flange 45.

At its opposite end, the lever 50 is formed with a fork 52 to which is secured the upper end of a rod 53. A collar 54 is secured to said rod 53 adacent the lower end thereof, said collar being adjustable on said rod. The plate 29 carries a bracket 55 formed with a yoke 59 loosely embracing the rod 53, and freely slidable with respect thereto. It will be clear that, as the plate 29 is moved downwardly, the yoke 59 will come into contact with the upper surface of the collar 54 and, upon continued movement of said plate, said yoke will cooperate with said collar to move the rod 53 downwardly, thereby rocking the lever 59 to disengage the clutch element 44 from the sprocket 43.

Said bracket 55 further carries a stud 5! in which is adjustably received a rod 59, said rod being aligned with an aperture 58 formed in the upper surface of the base 3| for a purpose later to be stated. Said rod carries a collar 59 which supports a spring 69 which, in turn, supports a collar 6| which is freely slidable on said rod 58. A yoke 62 is formed at one end of a lever 63 pivoted at 94 to the base 3|, and said yoke loosely embraces the rod 58, said yoke being positioned in the path of the collar 6|. The opposite arm of the lever 93 carries a hub 65 in which the rod 53 is secured. As the plate 29 moves upwardly, the rod 58 will be carried with it, and the collar 6| will be moved into engagement with the lower surface of the yoke 62. Further upward movement of said plate or carriage 29 will cause a certain amount of compression of the spring 69; and when the compression of said spring overcomes the resistance to movement of the rod 53, said rod will be moved downwardly to rock the lever 59 to disengage the clutch element 9 from the sprocket 43.

A casing 96 is mounted upon the upper surface of the base 3|, and a secondary casing 61 is, in the illustrated embodiment of my invention, secured to the upper end of the casing 69 by bolts 98, or the like. The upper end of the rod 42 projects through a suitable aperture in the top of said casing ill; and a portion of the top of said casing 91 is open, as is clearly indicated in Figs. 3 and 4. The open portion of said casing 91 is normally closed by a cover 69 secured to said casing by bolts I9 or the like.

Said cover 89 is pierced by an aperture II through which projects the upper squared end 12 of a pin I3, the lower reduced end I4 of which is received in a suitable socket I5 in an oscillable shaft I9 mounted in suitable bearings in said base 3|.

Referring, now, to Figs. 4 to 8 inclusive, it will be seen that an arm I1 is provided with a hub I8 which is sleeved over, and keyed to, the upper end of said shaft "l9. At its free end, said arm is provided with a hub I9 in which is journaled a pin 8|. A bore 89, formed at one end of an arm 82, is sleeved over the upper end of the pin BI, and said arm 82 is keyed to said pin 8|. A pin 83 secures to the free end of said arm 82 one end of a link 89, the opposite end of said link being secured by a pin 85 to the free end of an arm 86, the opposite end of said arm being formed with a hub 81, sleeved on and keyed to the pin I3.

A collar 88 (which, in the illustrated embodiment of my invention, comprises two elements) is keyed or pinned to the pin 8|, being positioned between said arm 82 and the hub I9. Said collar 98 is provided with diametrically-opposite fingers 89 and 9| positioned in a common horizontal plane; and is further provided with a finger 99,

.angularly removed somewhat from the finger 9|, and positioned in a lower plane.

The pin 9| extends entirely through the hub I9, and projects below the same; and said pin carries at its lower end a pawl member 92 provided with substantially oppositely-extending fingers 93 and 94. It will be seen that the pawl 92 comprises a double-ended pawl. It will likewise be seen that the position of said pawl may be manually adjusted by applying the crank 48 to the squared end I2 of the pin l3, and shifting said crank. Such movement of the crank is transmitted from the pin I3 through the arm 86, link 84, and arm 82, to the pin BI, and so to the pawl 92 which 15 fixedly carried on said pin 8|.

A sprocket 95 is loosely mounted on the shaft '56, and said sprocket is formed with an upwardlyextending hub 99 upon which is keyed a ratchet wheel 9'! having teeth 98 with which the finger 93 of the pawl 92; is cooperable to rotate said ratchet wheel in a clockwise direction, only, as viewed in Fig. 4. #A second ratchet wheel 99 is likewise keyed to said hub 96, and said ratchet wheel 99 is formed with teeth I 99 with which the finger 99 of the pawl 92 is cooperable to move said ratchet wheel 99 in a counter-clockwise direction only, as viewed in Fig. 4.

It will be clear that the finger 93 and ratchet wheel 97 comprise a one-way clutch; and that the finger 94 and ratchet wheel 99 comprise an oppositely-acting one-way clutch. It will also be clear that the wheels 91 and 99, being mutually keyed to the hub 99, constitute a single ratchet wheel having oppositely-pitched teeth. Thus it may be conceived that the wheels 91 and 99 constitute a single ratchet with which cooperates a single double-ended pawl; or it may be conceived that the wheels 91 and 99 constitute separate ratchet wheels with which cooperate two pawls 99 and 94.

A chain I9I forms a driving connection between the sprocket 95 and the sprocket 93; and I prefer to provide a tensioning sprocket Hi2, which, in the illustrated embodiment of my invention, is rotatably mounted upon an axle I93 which is adjustably mounted in a slideway I94 formed in a bracket I95 suitably mounted within the casing 91. It will be seen that adjustment of the axle I93 in the slideway I94 will result in tightening or loosening the chain I9I,

A bracket I99 suitably formed in or mounted in the casing 61, is formed to provide a slideway I9'I which is concentric with the shaft l9.

A bracket I 98 is adjustably secured in said slideway I 91 by clamping means I99. Said bracket I 98 carries an arm II9 having a finger III which is engageable with the finger 99, at one extremity of the path of movement of the arm 11, to move the pawl 92 into, and to hold said pawl in, the position of Fig. 4, wherein said pawl 92 is out of engagement with both sets of teeth I99 and 99. Said bracket I98 further carries a finger I I2 which is cooperable with the finger 99 for a purpose later to be described.

A second bracket H3 is adjustably secured in the slideway I91 by clamping means IM. Said bracket H3 carries a stud II5 upon which is pivotally mounted a lever IIB, one end of which is formed with a finger II'I cooperable, at times, with the finger 9i to move the pawl 92 into the position of Fig. 6. A spring II8 cooperates with the opposite arm of said lever H5, and tends to rotate said lever in a counterclockwise direction as viewed in Fig. 4; and a second spring II9 engages said last-mentioned arm of said lever HE,

said spring II9 tending to rotate said lever H6 in a clockwise direction. The effective strength of the spring H9 is adjustable through the medium of a screw I20.

A third bracket |2I is adjustably mounted in the slideway I01 through. the medium of clamping means I22. Said bracket I2I carries a stud I23 upon which is pivotally mounted a lever I24, one end of said lever being formed to provide a finger I25, cooperable with the finger 90 at times, to move the pawl 92 into the position of Fig. 7. The opposite arm I26 of said lever I24 is engaged by a spring I21 which tends to rotate said lever in a clockwise direction as viewed in Fig. 4, there being provided a stop on the bracket I 2| to limit the movement of said lever I24 under the influence of the spring I21.

A fourth bracket I28 is adjustably mounted in the slideway I 01 through the medium of clamping means I29. Said bracket I28 carries an arm I30 terminating in a finger I3I, cooperable, at times, with a finger I43 formed on the collar 88, to move the pawl 92 into neutral position. Fig. 8 illustrates the engagement of said finger I3I with said finger I43. As is clearly shown in Fig. 8, the collar 88 is formed with a surface I44 adapted to be moved, by the engagement of said fingers I3I and I43, into engagement with the adjacent surface of the arm I30, whereby said pawl 92 will be positively held in neutral position, so long as said surfaces are in engagement.

At its lower end, the shaft 16 carries an arm I32, said arm being formed with a plurality of apertures adapted to receive a pin for securing to said arm one end of a link I33. Said link I33 may be selectively associated with any one of said apertures in said arm I32, thereby varying the length of stroke of said arm. The opposite end of the link I33 is secured to an arm I34 fast on the shaft 20; and said arm I34 is also formed for adjustable association therewith of said link I33.

The base 3| is formed with a plurality of slots I39, I40 and MI for the reception of bolts for securing said base to the skeleton II of the spinning frame; said slots being elongated in. order to permit slight variations in the position of said base with respect to said skeleton. The base 3| is further provided with a plurality of apertures I42 for the reception of bolts to secure said base to the floor. The base 3| is further provided with an arm or brace I35, the free end of which is adapted to be secured to another portion of the skeleton II. Said brace I35 carries a bearing I36 for supporting the outer end of the shaft I9. As is clearly shown in Fig. 3, the brace I35 is secured to the base 3| by means of bolts I31 adjustably positioned in a vertically elongated slot I38 in said base 3 I.

In Fig. 9 there is illustrated in detail my means for holding the pawl 92 in adjusted position. Hub 19 of the arm 11 is formed with a socket I45 terminating, adjacent its upper end, in a reduced bore I49, whereby a downwardly facing shoulder I46 is formed. Reciprocably mounted in the socket I45 is a plunger I41, said plunger being surrounded by a spring I48, and the upper end I50 of said plunger extending into and being guided in, said reduced bore I49. At its lower end, the plunger I41 carries an enlarged head I5I formed with a cone surface I52 at its lower end. The pawl 92 is formed, in its upper surface, with three conical depressions I 53, said depressions being arranged concentrically with respect to the pin 8 I. When the pawl 92 is in the position illustrated in Fig. 6, the conical end I52 of the plunger head I5I is solidly seated in the intermediate one of said three depressions I53, as illustrated in Fig. 9. When the pawl is in the position of Fig. '7, said plunger head is solidly seated in the left-hand depression I53, as seen from above. When the pawl is in the position of Fig. 4, the plunger head surface I 52 is entered in, but not solidly seated in, the right-hand depression I53, as viewed from above.

When the device of the present application is.

to be used with a spinning frame for filling winding, the control mechanism is set up as shown in Fig. 4. The carriage 29 will be in such a position that the speed ratio between the shaft 21 and the shaft I9 is an optimum for starting. With the carriage in that starting position, the rod 58 is adjusted in the sleeve 51 so that the upper end of said rod is positioned within the aperture 58, and flush with the upper surface of said base 3|. Thus, the rod 58 becomes an indicator whereby the operator may readily determine whether or not the transmission is in optimum starting position, in beginning future runs.

The arm 11 is in the position of Fig. 4, wherein the finger II I engages the finger 89 to hold the pawl end 94 just out of operative engagement with the teeth I 08; but in that position, the coned surface I52 of the plunger head I5I is engaged in the right-hand socket I53 so that, immediately upon release of the engagement between the fingers II I and 89, the pawl arm 94 will be forced, by the pressure of the spring I48, into operative engagement with the teeth I00.

The spinning frame being properly threaded, operation of the motor 28 is now started to drive the spinning frame at optimum low starting speed. As the spinning frame operates, the shaft 20 oscillates and, through the arm I34, link I33 and arm I32, the oscillation of the shaft 20 is transmitted to the shaft 16, and so to the arm 11. As the arm 11 moves in a counter-clockwise direction, as viewed in Fig. 4, the pawl arm 94 comes into engagement with the teeth I00 to move the ratchet wheel 99 in a counter-clockwise direction through substantially the full counter-clockwise stroke of said arm 11. Since the ratchet wheel 99 is keyed to the sprocket 95, that movement of said ratchet wheel will be transmitted to the sprocket 95, and so through the chain IOI, to the sprocket 43, whereby the shaft 35 is moved slightly in a counter-clockwise direction, as viewed from above. Such movement of the shaft 35 results in slight downward movement of the collar 33, and said collar carries with it the carriage 29 and motor 28. As the motor 28 moves downwardly, carrying with it shaft 21 and pulley 26, the belt 32 is tensioned to move the disc 23 slightly to the left, as viewed in Fig. 2.. Thus, the effective diameter of the pulley formed by the discs 22 and 23 is slightly decreased, whereby the speed of the shaft I 9, and consequently of the spinning frame as a whole, is slightly increased.

Upon its return stroke, the arm 11 carries with it the pawl 92, the arm 94 of said pawl clicking over the teeth I90 without causing movement of the ratchet wheel 99. During that return stroke, the clicking of the pawl arm 94 is permitted by reason of the fact that, as the pawl 92 moves slightly in a clockwise direction about the axis of the pin 8|, the corresponding coned surfaces of the socket I53 and the head I 5| cause the plunger head I5I to be cammed slightly upwardly. As the pawl arm 94 rides over the end of one of the teeth I00, the spring I48 forces the head |5I downwardly into the socket I53, thereby camming the pawl arm 94 back into contact with the surface of the next adjacent tooth.

As has been stated, during filling wind operation, the shaft 29 oscillates through a stroke of substantially constant length but of varying position. That is, the component of the stroke of the shaft 29 which results in counter-clockwise movement of the arm ll, as viewed in Fig. 4, is slightly longer than the return stroke of said shaft. Consequently, the arm ll, during its oscillation, advances in a counter-clockwise direction.

During such advance of the arm 71, the speed of the shaft I9 is gradually increased by stepby-step movement of the carriage 29 downwardly in response to counter-clockwise rotation of the shaft 35. The bracket H3 is so positioned that, at about the time when the building up of the inverted cone surfaces near the bottoms of the bobbins [2 has been completed, the finger II! will engage the finger 9| to shift the collar 88, pin 8| and pawl 92 into the position of Fig. 6. Such shifting, of course, involves the operation of camming the plunger head i! entirely out of the right-hand socket I53, and moving the pawl in a clockwise direction about the axis of the pin 8| to a position in which the plunger l5! will enter the intermediate socket I53. When said plunger head enters that socket, it acts to hold the pawl 92 in the position of Fig. 6, in which neither the arm 93 nor the arm 94 of the pawl engages the ratchet teeth 91 or I90.

So long as the pawl 92 is in the position of Fig. 6, the arm I! may oscillate without affecting the ratchet wheels 91 and 99 or the sprocket 95, and consequently without affecting the sprocket 43 and shaft 35. Consequently, the spinning frame will continue to operate at the optimum high speed which has been attained prior to the shifting of the pawl 92 into the position of Fig. 6.

Eventually, the arm 11, in continuing to advance, reaches a position at which the finger I25 contacts the finger 9B of the collar 88 to shift the pawl 92 into the position of Fig. 7, wherein the pawl arm 93 is in operative association with the teeth 98 of the ratchet wheel 91. Obviously, such shifting of the pawl involves the steps of camming the plunger head I5l out of the intermediate socket I53, and shifting the pawl into a position in which the plunger head l5! enters the left-hand socket I53.

With the pawl in its new position, the clockwise portion of the stroke of the arm 1! will be transmitted through the pawl arm 93 and ratchet wheel 91 to the sprocket 95, and so, through the chain it! and sprocket 93, to the shaft 35 to reduce the speed of the spinning frame by increasing the effective diameter of the pulley formed by the discs 22 and 23. The counter-clockwise portion of the stroke of the arm 91 will merely cause the pawl arm 93 to click over the teeth 98 of the ratchet wheel 91.

Thus, as the ratchet arm 'l'l oscillates, and progresses beyond the position of Fig. '7, the speed of the spinning frame will gradually be reduced during the period in which the cone surfaces are being formed adjacent the tops of the spindles. When the speed of the spinning frame has been reduced to an optimum low value, the arm T! reaches the position of Fig. 8, in which position the finger l3! engages the finger M3 to shift the pawl 92 again to neutral position, and any further operation of the organization is continued with the pawl 92 in its neutral position, the speed of the spinning frame being maintained at its low optimum.

When the filling of the bobbins is completed, the motor 23 is stopped, and the bobbins are doffed. The pawl 92 being in its neutral position it will be clear, that when the operator returns his ring rail it to its starting position, movement of the ring rail is transmitted through the rod 19, arm 2i, shaft 20, arm HG, link I33 and arm 532 to th shaft l9; whereby the arm "ii! is returned to its starting position. Obviously, the spring i2? permits the lever IM to swing hackwardly out of the way of the finger 90, and similarly, the lever H5 swings out of the way of finger 9!, during such return movement of the arm El. However, as the arm l1 approaches its starting position, the finger 90 engages the finger M2 on the bracket Hi8, and as the arm 11 moves beyond that position, such engagement results in shifting of the pawl 92 back into the position in which the arm 94 thereof is cooperatively engaged with the teeth 899 of the ratchet wheel 99, so that the machine is ready to start again. When the arm ll reaches the right-hand limit of its stroke, the finger 99 comes into contact with the finger ill, whereby the pawl arm 99 is moved just out of contact with said teeth 599. As has heretofore been explained, the spring M8 is, at this time, resiliently urging the arm 99 toward engagement with said teeth I99.

The reason for the provision of the cooperating fingers 89 and H I is that it is sometimes desirable to change the starting speed of the machine. If the operator has found that his original starting speed was slightly too fast or too slow, he may now adjust that starting speed by applying the crank 48 to the squared upper end of the shaft 42 and rotating said crank. Such rotation, of course, results in rotation of the sprocket 43 which, through the chain llll, drives the sprocket 95 to which are keyed ratchet wheels 91 and 99. It is, therefore, necessary that the pawl 92 be held out of engagement with the ratchet teeth during such adjustment.

Means has been provided whereby the operator may vary the position of the pawl 92 manually at any time during the operation of the machine, and without stopping the machine. If the crank 98 is applied to the squared upper end 72 of the pin 13, movement of said crank will be transmitted through the arm 86, link 84, arm 82, and pin 8! to the pawl.

When it is desired to use the herein disclosed drive and control mechanism is connection with a spinning frame for warp winding, the brackets H3 and Hi are removed from the machine, and the brackets E28 and I98 may be removed from the machine. The collar 54 is then suitably adjusted on the rod 53 to disengage the clutch member 44 from the sprocket 43 at an optimum high speed.

The pawl arm 95 is manually shifted into cooperative relation with the teeth I00 of the ratchet wheel 99 and, the carriage 29 being positioned to cause the motor 28 to drive the spinning frame at optimum low starting speed, the motor 28 is started.

In warp winding, the stroke of the arm 1'! is of varying length, but substantially unvarying position. Obviously, the full measure of the counter-clockwise portion of the stroke of said arm TI is transmitted, through the pawl arm 94, ratchet wheel 99, sprocket 95, chain I0], sprocket 33, clutch member 94, and shaft 42 to the threaded shaft 35. The speed of the spinning frame is thus gradually increased step-by-step, as the carriage 29 is moved downwardly. Eventually, and when optimum high speed position has been reached, engagement between the yoke 58 and the collar 54 will rock the lever to lift the clutch element 44 out of engagement with the sprocket 43. Obviously, thereafter the sprocket 43 will still be rotated step-by-step throughout the continued time of operation of the machine, but said sprocket will be ineffective to transmit movement to the shaft 35, so that the machine will continue to operate at optimum high speed.

After the wind has been completed, the operator manually shifts the pawl 92 into neutral position and then, applying the crank 48 to the upper end of the shaft 42, manually returns the carriage 29 to starting position, whereafter the cycle may be again started.

Collar 54 and the mechanism 59, 60, BI, 62, 63,- 64, 65 constitute safety means when the control mechanism is used in connection with a filling wind machine. When the mechanism is to be so used, the collar 54 is set at a position in which it will be engaged by the yoke 56 if the carriage 29 moves beyond an optimum high speed position. Thus, if through some accident, the finger II! should fail to shift pawl 92 into neutral position, a very slight following increase in speed would result in the disengagement of the clutch member 44 from the sprocket 43. Of. course, if that should happen, operation of the finger I25 to shift the pawl 92 into the position of Fig. 7 would be ineffective to cause a decrease in speed of the machine; so that, if the safety feature operates, it is necessary for the operator to stop his machine and cure the trouble which has caused the operation of such safety feature.

Correspondingly, if. the speed-reducing operation of the control should not be stopped by the cooperation of the fingers l3l and I43, continued upward movement of the carriage 29 would result in engagement of the yoke 62 by the collar 6|, and consequent disengagement of the clutch 44 from the sprocket 43.

I claim as my invention:

1. In a device of the class described, an oscillating shaft, a gear loosely mounted on said shaft, a ratchet wheel having oppositely-pitched teeth fixedly mounted coaxially on said gear, an arm fixed on said shaft and carrying a double-ended pawl for cooperation with said oppositely-pitched teeth, said pawl being adapted to assume, selectively, a position engaging said teeth in one direction, a position engaging said teeth in the opposite direction, or a position entirely out of engagement with said teeth, and a plurality of cam fingers cooperable with said pawl, during the cycle of operation of said arm, to shift said pawl automatically into and out of its various positions with respect to said ratchet.

2. In a device of the class described, a shaft, means for oscillating said shaft through a stroke of varying position, a gear loosely mounted on said shaft, a ratchet wheel having oppositelypitched teeth fixed to said gear, an arm rigid with said shaft, a double-ended pawl pivotally carried at the free end of said arm and cooperable with said ratchet wheel, and means automatically operable upon change in the position of said shaft stroke, to shift said pawl into a position to drive said ratchet in one direction only upon oscillation of said shaft, then into a position in which said pawl is ineffective to drive said ratchet, and then into a position to drive said ratchet in the opposite direction.

3. In a device of the class described, a shaft, a ratchet loosely mounted on said shaft and having oppositely-pitched teeth, an arm fast on said shaft, a double-ended pawl pivotally carried at the free end of said arm, a finger mounted adjacent said shaft and engageable with said pawl, at times, to move said pawl out of cooperative relation with said ratchet, a second finger mounted adjacent said shaft and engageable with said pawl, at times, to move one end of said pawl into cooperative relation with said ratchet, and a third finger mounted adjacent said shaft and engageable with said pawl, at times, to move the other end of said pawl into cooperative relation with said ratchet.

4. In a device of the class described, a shaft, an arm fixed on said shaft, means driving said shaft through an oscillatory stroke of substantially constant length but of progressively varying position whereby the free end of said arm, while oscillating, is driven through an arcuate path of greater length than said oscillating stroke, a ratchet wheel loosely mounted on said shaft, a pawl carried at the free end of said arm, and means mounted adjacent the path of the free end of said arm and cooperable with said pawl, upon operation of said shaft, to shift said pawl into and out of reversely cooperative relations with said ratchet.

5. In a device of the class described, a shaft, an arm fixed on said shaft, means for oscillating said shaft through a stroke of substantially constant length but of varying position whereby the free end of said arm, while oscillating, is driven through an arcuate path of greater length than said oscillating stroke, a ratchet wheel loosely mounted on said shaft, a pawl carried at the free end of said arm, means engageable with said pawl at one extremity of the path of said arm and operable during engagement thereof with said pawl, to hold said pawl out of cooperative relation with said ratchet, and other means engageable with said pawl at a point intermediate the ends of said path, and operable, upon such engagement, to shift said pawl into a new position out of cooperative relation with said ratchet.

6. In combination, a base, a carriage slidable on said base, a motor mounted on said carriage and having a shaft, a driven shaft, pulleys on said shafts, one of said pulleys being expansible,

and a belt providing a driving connection between said pulleys, an element movable to shift said carriage on said base, and means for controlling said element, comprising an oscillable shaft, means connecting said driven shaft to oscillate said oscillable shaft, a ratchet wheel 1 loosely mounted on said oscillable shaft and drivingly connected with said element, a pawl carried on said oscillable shaft, means associated with said pawl and operable, at times, to shift said pawl into operative engagement with said ratchet, whereby said oscillable shaft is connected to move said element step-by-step in one direction, and other means associated with said pawl and operable, at times, to shift said pawl out of operative engagement with said ratchet, whereby said oscillable shaft is rendered ineffective to move said element.

'7. In combination, a base, a carriage slidable on said base, a motor mounted on said carriage and having a shaft, a driven shaft, pulleys on said shafts, one of said pulleys being expansible and a belt providing a driving connection between said pulleys, an element movable to shift said carriage on said base, and means for controlling said element, comprising an oscillable shaft, means connecting said driven shaft to oscillate said oscillable shaft, a ratchet wheel loosely mounted on said oscillable shaft and drivin-gly connected with said element, a pawl carried on said oscillable shaft and movable into and out of operative engagement With said ratchet, said pawl, when engaged with said ratchet, connecting said oscillable shaft to move said element stepby-step in one direction, a second ratchet wheel loosely mounted on said oscillable shaft and likewise drivingly connected with said element, a second pawl carried on said oscillable shaft and movable into and out of operative engagement with said second ratchet, said second pawl, when engaged with said second ratchet, connecting said oscillable shaft to move said element step-bystep in the opposite direction, and means associated with said pawls and automatically operable, during the cycle of operation of the organization, to shift said pawls selectively and alternatively into and out of operative engagement with their respective ratchets.

PAUL B. REEVES. 

